U.S. patent application number 16/817041 was filed with the patent office on 2020-09-17 for compressor.
The applicant listed for this patent is LG Electronics Inc.. Invention is credited to Cheolhwan KIM, Kyungho LEE, Sangbaek PARK.
Application Number | 20200291779 16/817041 |
Document ID | / |
Family ID | 1000004737252 |
Filed Date | 2020-09-17 |
United States Patent
Application |
20200291779 |
Kind Code |
A1 |
LEE; Kyungho ; et
al. |
September 17, 2020 |
COMPRESSOR
Abstract
Disclosed is a scroll type compressor having an Oldham's ring
having an asymmetrical structure with respect to a long or minor
axis thereof.
Inventors: |
LEE; Kyungho; (Seoul,
KR) ; PARK; Sangbaek; (Seoul, KR) ; KIM;
Cheolhwan; (Seoul, KR) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
LG Electronics Inc. |
Seoul |
|
KR |
|
|
Family ID: |
1000004737252 |
Appl. No.: |
16/817041 |
Filed: |
March 12, 2020 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04C 15/06 20130101;
F04C 2/025 20130101; F04C 15/0073 20130101; F01C 17/066 20130101;
F05B 2250/33 20130101 |
International
Class: |
F01C 17/06 20060101
F01C017/06; F04C 15/00 20060101 F04C015/00 |
Foreign Application Data
Date |
Code |
Application Number |
Mar 12, 2019 |
KR |
10-2019-0027911 |
Claims
1. A compressor comprising: a casing; a driver coupled to an inner
surface of the casing and configured to rotate a rotation shaft;
and a compression assembly engaged with the rotation shaft and
configured to compress a refrigerant, wherein the compression
assembly includes: a fixed scroll coupled to the inner surface of
the casing; an orbiting scroll connected to the rotation shaft and
configured to orbit relative to the fixed scroll, a main frame
connected to the fixed scroll and at least partially receiving the
orbiting scroll, the main frame supporting the rotation shaft; and
a ring engaged with the orbiting scroll and the main frame to block
spinning of the orbiting scroll, wherein the ring is asymmetrical
with respect to at least one of a radial direction of the ring, a
minor axis of the ring, or a major axis of the ring.
2. The compressor of claim 1, wherein the ring is asymmetrical with
respect to the minor axis of the ring.
3. The compressor of claim 1, wherein the ring includes: a ring
body disposed between the orbiting scroll and the main frame,
wherein the rotation shaft extends through the ring body; a
plurality of scroll keys protruding from the ring body in a
direction along the minor axis and inserted into the orbiting
scroll; and a plurality of frame keys protruding from the ring body
in a direction along the major axis and inserted into the main
frame, wherein the ring body is asymmetrical such that a distance
of one of the plurality of scroll keys and one of the plurality of
frame keys is different from a distance between the one of the
plurality of scroll keys and another frame key of the plurality of
frame keys.
4. The compressor of claim 1, wherein the ring includes: a ring
body disposed between the orbiting scroll and the main frame,
wherein the rotation shaft extends through the ring body; a
plurality of scroll keys protruding from the ring body in a
direction along the minor axis and inserted into the orbiting
scroll; and a plurality of frame keys protruding from the ring body
in a direction along the major axis and inserted into the main
frame, wherein the ring body is asymmetrical such that a shortest
distance between one of the plurality of frame keys and a line
extending through the plurality of scroll keys is different from a
shortest distance between another of the plurality of frame keys
and the line extending through the plurality of scroll keys.
5. The compressor of claim 1, wherein the fixed scroll has a
discharge hole that is spaced apart from the rotation shaft and
configured to discharge the refrigerant, wherein the ring includes:
a ring body disposed between the orbiting scroll and the main
frame, wherein the rotation shaft extends through the ring body; a
plurality of scroll keys protruding from the ring body in a
direction along the minor axis and inserted into the orbiting
scroll; and a plurality of frame keys protruding from the ring body
in a direction along the major axis and inserted into the main
frame, wherein the ring body is asymmetrical such that one of the
plurality of frame keys spaced from a line extending through the
plurality of scroll keys by a larger spacing than the other frame
keys is closer to the discharge hole.
6. A compressor comprising: a casing a driver coupled to an inner
surface of the casing and configured to rotate a rotation shaft;
and a compression assembly engaged with the rotation shaft and
configured to compress a refrigerant, wherein the compression
assembly includes: a fixed scroll including a discharge hole that
is spaced apart from the rotation shaft; an orbiting scroll
connected to the rotation shaft and configured to orbit relative to
the fixed scroll; a main frame connected to the fixed scroll and at
least partially receiving the orbiting scroll, the main frame
supporting the rotation shaft; a ring engaged with the orbiting
scroll and the main frame to block spinning of the orbiting scroll,
wherein the ring has a major axis and a minor axis; and a
backpressure seal seated on the orbiting scroll within the ring,
wherein the backpressure seal is positioned eccentrically relative
to the rotation shaft to apply a back pressure toward the discharge
hole, wherein of both ends corresponding to the long axis of the
ring, one end of the ring spaced apart from the back pressure seal
is provided closer to the minor axis of the ring than the other end
of the ring.
7. The compressor of claim 6, wherein the ring includes a ring body
having the major axis and the minor axis, wherein the major axis is
a line extending between a center of the backpressure seal and a
center of the rotation shaft, wherein an end of the major axis of
the ring body that is spaced farther from the eccentric
backpressure seal than an opposite end of the major axis of the
ring body is closer to the minor axis than the opposite end of the
major axis of the ring body.
8. The compressor of claim 7, wherein the end of the major axis of
the ring body is provided closer to the minor axis of the ring body
than the opposite end of the major axis of the ring body, and
wherein the closer distance corresponds to a distance from which
the center of the backpressure seal is spaced apart from the center
of the rotation shaft.
9. The compressor of claim 7, wherein the ring includes a plurality
of frame keys protruding from the ring body in a direction along
the major axis and inserted into the main frame, wherein the ring
body is constructed such that one of the plurality of frame keys is
closer to the backpressure seal than another of the plurality of
frame keys.
10. The compressor of claim 9, wherein the plurality of frame keys
includes a first frame key and a second frame key, the first frame
key being spaced farther from the center of the backpressure seal
than the second frame key, and wherein the ring body is constructed
such that a first distance between the first frame key and the
minor axis is shorter than a second distance between the second
frame key and the minor axis, thereby reducing a distance between
the first frame key and the second frame key.
11. The compressor of claim 10, wherein a length by which the first
distance is shorter than the second distance is equal to a distance
between the center of the backpressure seal and the center of the
rotation shaft.
12. The compressor of claim 7, wherein the minor axis is
perpendicular to the major axis, and wherein a distance between
opposite ends in the minor axis of the ring body is equal to a
diameter of the backpressure seal.
13. A compressor comprising: a casing; a driver coupled to an inner
surface of the casing and configured to rotate a rotation shaft;
and a compression assembly engaged with the rotation shaft and
configured to compress a refrigerant, wherein the compression
assembly includes: a fixed scroll coupled to the inner surface of
the casing; an orbiting scroll connected to the rotation shaft and
configured to orbit relative to the fixed scroll; a main frame
connected to the fixed scroll and at least partially receiving the
orbiting scroll, the main frame supporting the rotation shaft; and
a ring engaged with the orbiting scroll and the main frame to
reduce spinning of the orbiting scroll, wherein the ring includes:
a ring body having a major axis and a minor axis that is different
in length from the major axis, and a plurality of frame keys
protruding from the ring body in a direction along the major axis
and inserted into the main frame, wherein the main frame includes:
a main end plate through which the rotation shaft extends, a main
side plate extending along a circumference of the main end plate
and configured to receive the ring body, and a plurality of main
key grooves defined in the main end plate, wherein the plurality of
frame keys of the ring are inserted into, and movable linearly
along, the plurality of main key grooves, respectively, wherein the
plurality of main key grooves are arranged asymmetrically about the
rotation shaft.
14. The compressor of claim 13, wherein the main frame further
includes a collection channel configured to receive an oil, wherein
the channel is recessed at a face of the main side plate, wherein
at least one of the plurality of main key grooves overlaps the
collection channel in a radial direction of the rotation shaft.
15. The compressor of claim 13, wherein at least one of the
plurality of main key grooves is spaced apart from a peripheral
surface of the main side plate toward the rotation shaft by a
larger distance than another of the plurality of main key
grooves.
16. A compressor comprising: a casing; a driver coupled to an inner
surface of the casing, and configured to rotate a rotation shaft;
and a compression assembly engaged with the rotation shaft and
configured to compress a refrigerant, wherein the compression
assembly includes: a fixed scroll including a discharge hole; an
orbiting scroll connected to the rotation shaft and configured to
orbit relative to the fixed scroll; a main frame connected to the
fixed scroll and at least partially receiving the orbiting scroll,
the main frame supporting the rotation shaft; an Oldham's ring
engaged with the orbiting scroll and the main frame to reduce
spinning of the orbiting scroll; and a backpressure seal seated on
the orbiting scroll within the Oldham's ring, wherein the
backpressure seal is positioned eccentrically relative to the
rotation shaft to apply a back pressure toward the discharge hole,
wherein the Oldham's ring includes: a ring body having a major axis
and a minor axis that is different in length from the major axis,
and a plurality of frame keys protruding from the ring body in a
direction along the major axis and inserted into the main frame,
wherein the plurality of frame keys are arranged to be inclined
relative to a line extending between a center of the backpressure
seal and a center of the rotation shaft.
17. The compressor of claim 16, wherein the main frame includes: a
main end plate through which the rotation shaft extends; a main
side plate extending along a circumference of the main end plate
and configured to receive the ring body; and a plurality of main
key grooves defined in the main end plate, wherein the plurality of
frame keys of the Oldham's ring are inserted into, and movable
linearly along, the main key grooves respectively, wherein the main
side plate has a circular shape configured to prevent the plurality
of frame keys from colliding with the main side plate so that the
main side plate is free of a collision-prevention groove.
18. The compressor of claim 1, wherein the ring is an Oldham's
ring.
19. The compressor of claim 6, wherein the ring is an Oldham's
ring.
20. The compressor of claim 13, wherein the ring is an Oldham's
ring.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] This application claims the benefit of Korean Patent
Application No. 10-2019-0027911, filed on Mar. 12, 2019, which is
hereby incorporated by reference as when fully set forth
herein.
BACKGROUND
Field
[0002] The present disclosure relates to a compressor. More
specifically, the present disclosure relates to a scroll type
compressor in which a structure of an Oldham's ring that prevents
spinning of an orbiting scroll is changed to reduce a weight
thereof and to enlarge an oil collection channel.
Discussion of the Related Art
[0003] Generally, a compressor is an apparatus applied to a
refrigeration cycle such as a refrigerator or an air conditioner,
which compresses refrigerant to provide work necessary to generate
heat exchange in the refrigeration cycle.
[0004] The compressors may be classified into a reciprocating type,
a rotary type, and a scroll type based on a scheme for compressing
the refrigerant. Among these, the scroll type compressor performs
an orbiting motion by engaging an orbiting scroll with a fixed
scroll fixed in an internal space of a sealed container to define a
compression chamber between a fixed wrap of the fixed scroll and an
orbiting wrap of the orbiting scroll.
[0005] Compared with other types of the compressor, the scroll type
compressor may obtain a relatively high compression ratio because
the refrigerant is continuously compressed through the scrolls
engaged with each other, and may obtain a stable torque because
suction, compression, and discharge of the refrigerant proceed
smoothly. For this reason, the scroll type compressor is widely
used for compressing the refrigerant in the air conditioner and the
like.
[0006] Referring to US Patent Application Publication No.
2017/0067466, a conventional scroll type compressor includes a
casing forming an outer shape of the compressor and having a
discharging portion for discharging refrigerant, a compression
assembly fixed to the casing to compress the refrigerant, and a
driver fixed to the casing to drive the compression assembly, and
the compression assembly and the driver are coupled to a rotation
shaft that is coupled to the driver and rotates.
[0007] The compression assembly includes a fixed scroll fixed to
the casing and having a fixed wrap, and an orbiting scroll
including an orbiting wrap operated in a state of being engaged
with the fixed wrap by the rotation shaft. Such the conventional
scroll type compressor includes the rotation shaft eccentric, and
the orbiting scroll fixed to the eccentric rotation shaft and
rotating. Thus, the orbiting scroll orbits along the fixed scroll
and compresses the refrigerant.
[0008] The conventional scroll type compressor further includes an
Oldham's ring that prevent the orbiting scroll from spinning while
being engaged with the fixed scroll.
[0009] FIGS. 1A and 1B show a structure of the Oldham's ring
installed in a conventional scroll type compressor.
[0010] Referring to FIG. 1A, a compression assembly of the
conventional scroll type compressor further includes a main frame
310 mounted on a fixed scroll to accommodate an orbiting scroll
therein. The main frame 310 may include a main end plate 311
through which a rotation shaft passes, and a main side plate 312
protruding from an outer circumferential face of the main end plate
311 and seated on the fixed scroll.
[0011] The main end plate 311 may accommodate therein a main shaft
receiving portion 318 through which the rotation shaft penetrates,
and a backpressure seal 350 provided on an outer circumferential
face of the main shaft receiving portion 318 to provide a back
pressure to the orbiting scroll. In this connection, a discharge
hole through which refrigerant discharges from the fixed scroll is
laterally spaced from a center 318a of the rotation shaft, so a
center 350a of the backpressure seal may be eccentrical relative to
the main shaft receiving portion 318.
[0012] The Oldham's ring 700 may be constructed to be received in
the main end plate 312.
[0013] The Oldham's ring 700 may include a ring body 710 provided
to receive the backpressure seal 350 and a key 720 inserted from
the ring body 710 into the main frame or orbiting scroll. The key
720 may be constructed to protrude along each of a major axis and a
minor axis of the ring body 710. For example, the key 720
protruding along the major axis of the ring body may be constructed
to be inserted into a main key groove 312a recessed in the main end
plate 311. The key 720 protruding along the minor axis of the ring
body may be constructed to protrude toward the orbiting scroll
330.
[0014] In this connection, the main key grooves 312a may be
arranged in a symmetrical manner with each other respect to the
main shaft receiving portion 318. Accordingly, the Oldham's ring
700 may reciprocate along the main key grooves 312a.
[0015] Referring to FIG. 1B, the orbiting scroll 330 may include a
seal groove 336 in which the backpressure seal is installed, and an
orbiting shaft receiving portion 338 through which the rotation
shaft passes. Further, the orbiting scroll 330 may include an
orbiting key groove 335 into which the key 720 of the Oldham's ring
is inserted. The orbiting key groove 335 may be spaced from the
main key groove 315 at an 90 degrees angular spacing. The orbiting
key grooves 335 may be in the same line with an extension line D
between a center 318a of the main shaft receiving portion and a
center 350a of the backpressure seal.
[0016] Thus, the Oldham's ring is constructed such that the key 720
reciprocates along the main key groove 315 and the orbiting key
groove 335, and is prevented from rotating. As a result, the
orbiting scroll may be prevented from spinning.
[0017] Referring back to FIG. 1A, in the conventional scroll type
compressor, the major axis of the Oldham's ring 700 bisects the
minor axis equally, and the minor axis thereof bisects the major
axis equally. In other words, a distance L1 of the Oldham's ring
700 between one of the keys 720 inserted into the main key grooves
and a center of an extension line of a line between the keys 720
inserted into the orbiting scroll is equal to a distance L2 of the
Oldham's ring 700 between the other of the keys 720 inserted into
the main key grooves and the center of an extension line of a line
between the keys 720 inserted into the orbiting scroll.
[0018] Further, the main frame of the conventional scroll type
compressor further includes a collision-prevention groove 312a so
that the key 720 inserted into the main key groove and the main
side plate 312 may be prevented from colliding with each other. As
a result, an inner peripheral surface of the main side plate 312 is
not continuous due to the collision-prevention groove 312a, thereby
reducing the compression efficiency in compressing the refrigerant.
Further, due to the collision-prevention groove 312a, a pressure
gradient occurs inside the main frame, thus causing noise or
vibration.
[0019] Further, in the conventional scroll type compressor, an oil
collection channel 310a defined in an outer circumferential face of
the main frame to collect oil separated from the refrigerant should
be constructed to be spaced apart from the main key groove and the
collision-prevention groove 312a. In this connection, the main side
plate has a plurality of main holes 317 defined therein through
which the refrigerant flows, so that an area of the collection
channel 310a should be reduced. As a result, there was a problem
that collection efficiency of the oil is lowered.
[0020] Further, the conventional scroll type compressor has a
problem that the Oldham's ring 700 has a symmetrical structure with
respect to a center thereof and occupies a large area and has a
relatively large weight so that a load applied to the driver
increases and noise increases.
[0021] Further, reducing a thickness or changing a material of the
Oldham's ring 700 caused a decrease in strength thereof such that
reliability of the Oldham's ring could not be guaranteed. Thus,
there was a limitation that the Oldham's ring 700 having a
structure with a relatively large area should be employed.
SUMMARY
[0022] A purpose of the present disclosure is to provide a
compressor having an Oldham's ring having an asymmetrical structure
along a long or minor axis thereof.
[0023] A purpose of the present disclosure is to provide a
compressor in which an area occupied by the Oldham's ring may be
reduced while maintaining a thickness of the Oldham's ring.
[0024] A purpose of the present disclosure is to provide a
compressor in which an inner face of the main frame housing the
Oldham's ring may be prevented from being depressed or
protruding.
[0025] A purpose of the present disclosure is to provide a
compressor in which an area of an oil collection channel defined in
a main frame may be increased by reducing an area occupied by the
Oldham's ring.
[0026] A purpose of the present disclosure is to provide a
compressor in which a weight of an Oldham's ring may be reduced by
reducing a total area thereof while maintaining a thickness of the
Oldham's ring.
[0027] A purpose of the present disclosure is to provide a
compressor in which grooves in which an Oldham's ring is coupled to
a main scroll are defined at a line inclined relative to a line
extending between a backpressure seal and a rotation shaft, thereby
to secure a moving space of the Oldham's ring to keep an inner
circumferential face of the main scroll to be continuously
circular.
[0028] Purposes of the present disclosure are not limited to the
above-mentioned purpose. Other purposes and advantages of the
present disclosure as not mentioned above may be understood from
following descriptions and more clearly understood from embodiments
of the present disclosure. Further, it will be readily appreciated
that the purposes and advantages of the present disclosure may be
realized by features and combinations thereof as disclosed in the
claims.
[0029] To accomplish the purposes above and other purposes,
particular embodiments described herein include a compressor that
includes a casing, a driver, and a compression assembly. The driver
may be coupled to an inner surface of the casing and configured to
rotate a rotation shaft. The compression assembly may be engaged
with the rotation shaft and configured to compress a refrigerant.
The compression assembly may include a fixed scroll, an orbiting
scroll, a main frame, and a ring. The fixed scroll may be coupled
to the inner surface of the casing. The orbiting scroll may be
connected to the rotation shaft and configured to orbit relative to
the fixed scroll. The main frame may be connected to the fixed
scroll and at least partially receiving the orbiting scroll, the
main frame supporting the rotation shaft. The ring may be engaged
with the orbiting scroll and the main frame to block spinning of
the orbiting scroll. The ring may be asymmetrical with respect to
at least one of a radial direction of the ring, a minor axis of the
ring, or a major axis of the ring.
[0030] In some implementations, the system can optionally include
one or more of the following features. The ring may be an Oldham's
ring. The ring may be asymmetrical with respect to the minor axis
of the ring. For example, the ring may include a ring body, a
plurality of scroll keys, and a plurality of frame keys. The ring
body may be disposed between the orbiting scroll and the main
frame. The rotation shaft may extend through the ring body. The
plurality of scroll keys may protrude from the ring body in a
direction along the minor axis and be inserted into the orbiting
scroll. The plurality of frame keys may protrude from the ring body
in a direction along the major axis and be inserted into the main
frame. The ring body may be asymmetrical such that a distance of
one of the plurality of scroll keys and one of the plurality of
frame keys is different from a distance between the one of the
plurality of scroll keys and another frame key of the plurality of
frame keys. In other examples, the ring may include a ring body, a
plurality of scroll keys, and a plurality of frame keys. The ring
body may be disposed between the orbiting scroll and the main
frame. The rotation shaft may extend through the ring body. The
plurality of scroll keys may protrude from the ring body in a
direction along the minor axis and be inserted into the orbiting
scroll. The plurality of frame keys may protrude from the ring body
in a direction along the major axis and be inserted into the main
frame. The ring body may be asymmetrical such that a shortest
distance between one of the plurality of frame keys and a line
extending through the plurality of scroll keys is different from a
shortest distance between another of the plurality of frame keys
and the line extending through the plurality of scroll keys. In yet
other examples, the fixed scroll may have a discharge hole that is
spaced apart from the rotation shaft and configured to discharge
the refrigerant. The ring may include a ring body, a plurality of
scroll keys, and a plurality of frame keys. The ring body may be
disposed between the orbiting scroll and the main frame. The
rotation shaft may extend through the ring body. The plurality of
scroll keys may protrude from the ring body in a direction along
the minor axis and be inserted into the orbiting scroll. The
plurality of frame keys may protrude from the ring body in a
direction along the major axis and be inserted into the main frame.
The ring body may be asymmetrical such that one of the plurality of
frame keys spaced from a line extending through the plurality of
scroll keys by a larger spacing than the other frame keys is closer
to the discharge hole.
[0031] Particular embodiments described herein include a compressor
that may include a casing, a driver, and a compression assembly.
The driver may be coupled to an inner surface of the casing and
configured to rotate a rotation shaft. The compression assembly may
be engaged with the rotation shaft and configured to compress a
refrigerant. The compression assembly may include a fixed scroll,
an orbiting scroll, a main frame, a ring, and a backpressure seal.
The fixed scroll may include a discharge hole that is spaced apart
from the rotation shaft. The orbiting scroll may be connected to
the rotation shaft and configured to orbit relative to the fixed
scroll. The main frame may be connected to the fixed scroll and at
least partially receiving the orbiting scroll. The main frame may
support the rotation shaft. The ring may be engaged with the
orbiting scroll and the main frame to block spinning of the
orbiting scroll. The ring may have a major axis and a minor axis.
The backpressure seal may be seated on the orbiting scroll within
the ring. The backpressure seal may be positioned eccentrically
relative to the rotation shaft to apply a back pressure toward the
discharge hole. Of both ends corresponding to the long axis of the
ring, one end of the ring spaced apart from the back pressure seal
may be provided closer to the minor axis of the ring than the other
end of the ring.
[0032] In some implementations, the system can optionally include
one or more of the following features. The ring may be an Oldham's
ring. The ring may include a ring body having the major axis and
the minor axis. The major axis may be a line extending between a
center of the backpressure seal and a center of the rotation shaft.
An end of the major axis of the ring body that is spaced farther
from the eccentric backpressure seal than an opposite end of the
major axis of the ring body is closer to the minor axis than the
opposite end of the major axis of the ring body. The end of the
major axis of the ring body may be provided closer to the minor
axis of the ring body than the opposite end of the major axis of
the ring body. The closer distance corresponds to a distance from
which the center of the backpressure seal is spaced apart from the
center of the rotation shaft. The ring may include a plurality of
frame keys protruding from the ring body in a direction along the
major axis and inserted into the main frame. The ring body may be
constructed such that one of the plurality of frame keys is closer
to the backpressure seal than another of the plurality of frame
keys. The plurality of frame keys may include a first frame key and
a second frame key. The first frame key may be spaced farther from
the center of the backpressure seal than the second frame key. The
ring body may be constructed such that a first distance between the
first frame key and the minor axis is shorter than a second
distance between the second frame key and the minor axis, thereby
reducing a distance between the first frame key and the second
frame key. A length by which the first distance is shorter than the
second distance is equal to a distance between the center of the
backpressure seal and the center of the rotation shaft. The minor
axis may be perpendicular to the major axis. A distance between
opposite ends in the minor axis of the ring body may be equal to a
diameter of the backpressure seal.
[0033] Particular embodiments described herein include a compressor
that may include a casing, a driver, and a compression assembly.
The driver may be coupled to an inner surface of the casing and
configured to rotate a rotation shaft. The compression assembly may
be engaged with the rotation shaft and configured to compress a
refrigerant. The compression assembly may include a fixed scroll,
an orbiting scroll, a main frame, and a ring. The fixed scroll may
be coupled to the inner surface of the casing. The orbiting scroll
may be connected to the rotation shaft and configured to orbit
relative to the fixed scroll. The main frame may be connected to
the fixed scroll and at least partially receive the orbiting
scroll, the main frame supporting the rotation shaft. The ring may
be engaged with the orbiting scroll and the main frame to reduce
spinning of the orbiting scroll. The ring may include a ring body
and a plurality of frame keys. The ring body may have a major axis
and a minor axis that is different in length from the major axis.
The plurality of frame keys may protrude from the ring body in a
direction along the major axis and be inserted into the main frame.
The main frame may include a main end plate, a main side plate, and
a plurality of main key grooves. The main end plate is configured
so that the rotation shaft extends through the main end plate. The
main side plate may extend along a circumference of the main end
plate and be configured to receive the ring body. The plurality of
main key grooves may be defined in the main end plate. The
plurality of frame keys of the ring may be inserted into, and
movable linearly along, the plurality of main key grooves,
respectively. The plurality of main key grooves may be arranged
asymmetrically about the rotation shaft.
[0034] In some implementations, the system can optionally include
one or more of the following features. The ring may be an Oldham's
ring. The main frame may include a collection channel configured to
receive an oil. The channel may be recessed at a face of the main
side plate. At least one of the plurality of main key grooves may
overlap the collection channel in a radial direction of the
rotation shaft. At least one of the plurality of main key grooves
may be spaced apart from a peripheral surface of the main side
plate toward the rotation shaft by a larger distance than another
of the plurality of main key grooves.
[0035] Particular embodiments described herein include a compressor
that may include a casing, a driver, and a compression assembly.
The driver may be coupled to an inner surface of the casing, and
configured to rotate a rotation shaft. The compression assembly may
be engaged with the rotation shaft and configured to compress a
refrigerant. The compression assembly may include a fixed scroll,
an orbiting scroll, a main frame, an Oldham's ring, and a
backpressure seal. The fixed scroll may include a discharge hole.
The orbiting scroll may be connected to the rotation shaft and
configured to orbit relative to the fixed scroll. The main frame
may be connected to the fixed scroll and at least partially receive
the orbiting scroll. The main frame may support the rotation shaft.
The Oldham's ring may be engaged with the orbiting scroll and the
main frame to reduce spinning of the orbiting scroll. The
backpressure seal may be seated on the orbiting scroll within the
Oldham's ring. The backpressure seal may be positioned
eccentrically relative to the rotation shaft to apply a back
pressure toward the discharge hole. The Oldham's ring may include a
ring body and a plurality of frame keys. The ring body may have a
major axis and a minor axis that is different in length from the
major axis. The plurality of frame keys may protrude from the ring
body in a direction along the major axis and inserted into the main
frame. The plurality of frame keys may be arranged to be inclined
relative to a line extending between a center of the backpressure
seal and a center of the rotation shaft.
[0036] In some implementations, the system can optionally include
one or more of the following features. The main frame may include a
main end plate, a main side plate, and a plurality of main key
grooves. The main end plate is configured such that the rotation
shaft extends through the main end plate. The main side plate may
extend along a circumference of the main end plate and be
configured to receive the ring body. The plurality of main key
grooves may be defined in the main end plate. The plurality of
frame keys of the Oldham's ring may be inserted into, and movable
linearly along, the main key grooves respectively. The main side
plate may have a circular shape configured to prevent the plurality
of frame keys from colliding with the main side plate so that the
main side plate is free of a collision-prevention groove.
[0037] In order to achieve the purposes, the present disclosure
provides an Oldham's ring having an asymmetrical structure adapted
to an eccentric position of a backpressure seal. As a result, at
least one of the Oldham's ring and the main frame may be reduced in
weight, and an area of an oil collection channel may be
increased.
[0038] In a compressor in accordance with the present disclosure,
one end of the Oldham's ring may be shortened to achieve the
asymmetrical structure. As a result, the weight may be reduced as
much as one end of the Oldham's ring is shortened
[0039] When the Oldham's ring is constructed in an oval or track
shape, the major axis may be shorter than the minor axis. As a
result, the effect of weight reduction may be maximized.
[0040] Furthermore, the major axis of the Oldham's ring may be
shortened by a distance between the center of the backpressure seal
and the center of the rotation shaft.
[0041] Further, the size of the frame key protruding from the major
axis portion of the Oldham's ring and coupled to the main frame may
be shortened in the major axis direction. As the Oldham's ring is
shortened, the size of the oil collection channel defined in the
main frame may increase correspondingly.
[0042] Further, in the compressor according to an embodiment of the
present disclosure, the inner circumferential surface of the main
frame may be maintained to be continuously circular, thereby to
increase the compression efficiency. This is because key grooves of
the main frame are asymmetrically arranged due to the reduced
length of the Oldham's ring, so that the main frame may be free of
a collision-prevention groove to prevent collision thereof with the
key of the Oldham's ring.
[0043] The features of the present disclosure may be applied to a
general scroll type compressor as well as to a shaft-through scroll
type compressor.
[0044] The present disclosure provides a shaft-through compressor
having an Oldham's ring having an asymmetrical structure rather
than an symmetrical structure.
[0045] The present disclosure may provide a mainframe collection
channel enlarged structure due to the Oldham's ring size
reduction.
[0046] Further, in accordance with the present disclosure, the
Oldham's ring may be constructed so that a distance between both
ends of the minor axis thereof may be reduced to a diameter of the
backpressure seal. Further, the Oldham's ring size reduction may
allow the inner circumference face of the main frame to be
continuously circular. Further, it may be possible to reduce the
weight of the main frame in a corresponding manner to a length by
which the Oldham's ring is shortened.
[0047] Further, in accordance with the present disclosure, the
Oldham's ring may be constructed such that the major axis of the
Oldham's ring is oriented in an inclined manner to the direction in
which the backpressure seal is eccentric.
[0048] The features of the above-described implantations may be
combined with other embodiments as long as they are not
contradictory or exclusive to each other.
[0049] The present disclosure has an effect of providing a
compressor having an Oldham's ring having an asymmetrical structure
along a long or minor axis thereof.
[0050] The present disclosure has an effect of providing a
compressor in which an area occupied by the Oldham's ring may be
reduced while maintaining a thickness of the Oldham's ring.
[0051] The present disclosure has an effect of providing a
compressor in which an inner face of the main frame housing the
Oldham's ring may be prevented from being depressed or
protruding.
[0052] The present disclosure has an effect of providing a
compressor in which an area of an oil collection channel defined in
a main frame may be increased by reducing an area occupied by the
Oldham's ring.
[0053] The present disclosure has an effect of providing a
compressor in which a weight of an Oldham's ring may be reduced by
reducing a total area thereof while maintaining a thickness of the
Oldham's ring.
[0054] The present disclosure has an effect of providing a
compressor in which grooves in which an Oldham's ring is coupled to
a main scroll are defined at a line inclined relative to a line
extending between a backpressure seal and a rotation shaft, thereby
to secure a moving space of the Oldham's ring to keep an inner
circumferential face of the main scroll to be continuously
circular.
[0055] Effects of the present disclosure are as follows but are
limited thereto.
BRIEF DESCRIPTION OF DRAWINGS
[0056] FIGS. 1A and 1B show a structure of the Oldham's ring of the
conventional compressor.
[0057] FIG. 2 illustrates a structure of a compressor according to
one embodiment of the present disclosure.
[0058] FIGS. 3A to 3C illustrate a method of operation of the
compressor according to one embodiment of the present
disclosure.
[0059] FIG. 4 illustrates an Oldham's ring of a compressor
according to one embodiment of the present disclosure.
[0060] FIGS. 5A and 5B illustrate an Oldham's ring of a compressor
according to another embodiment of the present disclosure.
[0061] FIG. 6 illustrates an Oldham's ring in accordance with
another embodiment of the present disclosure.
[0062] FIG. 7 illustrates an embodiment of a main scroll according
to FIG. 6.
DETAILED DESCRIPTIONS
[0063] For simplicity and clarity of illustration, elements in the
figures are not necessarily drawn to scale. The same reference
numbers in different figures denote the same or similar elements,
and as such perform similar functionality. Furthermore, in the
following detailed description of the present disclosure, numerous
specific details are set forth in order to provide a thorough
understanding of the present disclosure. However, it will be
understood that the present disclosure may be practiced without
these specific details. In other instances, well-known methods,
procedures, components, and circuits have not been described in
detail so as not to unnecessarily obscure aspects of the present
disclosure.
[0064] Examples of various embodiments are illustrated and
described further below. It will be understood that the description
herein is not intended to limit the claims to the specific
embodiments described. On the contrary, it is intended to cover
alternatives, modifications, and equivalents as may be included
within the spirit and scope of the present disclosure as defined by
the appended claims.
[0065] The terminology used herein is for the purpose of describing
particular embodiments only and is not intended to be limiting of
the present disclosure. As used herein, the singular forms "a" and
"an" are intended to include the plural forms as well, unless the
context clearly indicates otherwise. It will be further understood
that the terms "comprises", "comprising", "includes", and
"including" when used in this specification, specify the presence
of the stated features, integers, operations, elements, and/or
components, but do not preclude the presence or addition of one or
more other features, integers, operations, elements, components,
and/or portions thereof. As used herein, the term "and/or" includes
any and all combinations of one or greater of the associated listed
items. Expression such as "at least one of" when preceding a list
of elements may modify the entire list of elements and may not
modify the individual elements of the list.
[0066] It will be understood that, although the terms "first",
"second", "third", and so on may be used herein to describe various
elements, components, regions, layers and/or sections, these
elements, components, regions, layers and/or sections should not be
limited by these terms. These terms are used to distinguish one
element, component, region, layer or section from another element,
component, region, layer or section. Thus, a first element,
component, region, layer or section described below could be termed
a second element, component, region, layer or section, without
departing from the spirit and scope of the present disclosure.
[0067] In addition, it will also be understood that when a first
element or layer is referred to as being present "on" or "beneath"
a second element or layer, the first element may be disposed
directly on or beneath the second element or may be disposed
indirectly on or beneath the second element with a third element or
layer being disposed between the first and second elements or
layers. It will be understood that when an element or layer is
referred to as being "connected to", or "coupled to" another
element or layer, it may be directly on, connected to, or coupled
to the other element or layer, or one or more intervening elements
or layers may be present. In addition, it will also be understood
that when an element or layer is referred to as being "between" two
elements or layers, it may be the only element or layer between the
two elements or layers, or one or more intervening elements or
layers may be present.
[0068] Unless otherwise defined, all terms including technical and
scientific terms used herein have the same meaning as commonly
understood by one of ordinary skill in the art to which this
inventive concept belongs. It will be further understood that
terms, such as those defined in commonly used dictionaries, should
be interpreted as having a meaning that is consistent with their
meaning in the context of the relevant art and will not be
interpreted in an idealized or overly formal sense unless expressly
so defined herein.
[0069] Referring to FIG. 2, a scroll type compressor 10 according
to an embodiment of the present disclosure may include a casing 100
having therein a space in which fluid is stored or flows, a driver
200 coupled to an inner circumferential face of the casing 100 to
rotate a rotation shaft 230, and a compression assembly 300 coupled
to the rotation shaft 230 inside the casing and compressing the
fluid.
[0070] Specifically, the casing 100 may include a discharging
portion 121 through which refrigerant is discharged at one side.
The casing 100 may include a receiving shell 110 provided in a
cylindrical shape to receive the driver 200 and the compression
assembly 300 therein, a discharge shell 120 coupled to one end of
the receiving shell 110 and having the discharging portion 121, and
a sealing shell 130 coupled to the other end of the receiving shell
110 to seal the receiving shell 110.
[0071] The driver 200 includes a stator 210 for generating a
rotating magnetic field, and a rotor 220 disposed to rotate by the
rotating magnetic field. The rotation shaft 230 may be coupled to
the rotor 220 to be rotated together with the rotor 220.
[0072] The stator 210 has a plurality of slots defined in an inner
circumferential face thereof along a circumferential direction and
a coil is wound around the plurality of slots. Further, the stator
210 may be fixed to an inner circumferential face of the receiving
shell 110. A permanent magnet may be coupled to the rotor 220, and
the rotor 220 may be rotatably coupled within the stator 210 to
generate rotational power. The rotation shaft 230 may be pressed
into and coupled to a center of the rotor 220.
[0073] The compression assembly 300 may include a fixed scroll 320
coupled to the receiving shell 110 and disposed in a direction away
from the discharging portion 121 with respect to the driver 200, an
orbiting scroll 330 coupled to the rotation shaft 230 and engaged
with the fixed scroll 320 to define a compression chamber, and a
main frame 310 accommodating the orbiting scroll 330 therein and
seated on the fixed scroll 320 to form an outer shape of the
compression assembly 300.
[0074] As a result, the lower scroll type compressor 10 has the
driver 200 disposed between the discharging portion 120 and the
compression assembly 300. In other words, the driver 200 may be
disposed at one side of the discharging portion 120, and the
compression assembly 300 may be disposed in a direction away from
the discharging portion 121 with respect to the driver 200. For
example, when the discharging portion 121 is disposed on the casing
100, the compression assembly 300 may be disposed below the driver
200, and the driver 200 may be disposed between the discharging
portion 120 and the compression assembly 300.
[0075] Thus, when oil is stored in an oil storage space p of the
casing 100, the oil may be supplied directly to the compression
assembly 300 without passing through the driver 200. In addition,
since the rotation shaft 230 is coupled to and supported by the
compression assembly 300, a lower frame for rotatably supporting
the rotation shaft may be omitted.
[0076] In one example, the lower scroll type compressor 10 of the
present disclosure may be provided such that the rotation shaft 230
penetrates not only the orbiting scroll 330 but also the fixed
scroll 320 to be in face contact with both the orbiting scroll 330
and the fixed scroll 320.
[0077] As a result, an inflow force generated when the fluid such
as the refrigerant is flowed into the compression assembly 300, a
gas force generated when the refrigerant is compressed in the
compression assembly 300, and a reaction force for supporting the
same may be directly exerted on the rotation shaft 230.
Accordingly, the inflow force, the gas force, and the reaction
force may be exerted to a point of application of the rotation
shaft 230. As a result, since an upsetting moment does not act on
the orbiting scroll 320 coupled to the rotation shaft 230, tilting
or upsetting of the orbiting scroll may be blocked. In other words,
tilting in an axial direction of the tilting may be attenuated or
prevented, and the upsetting moment of the orbiting scroll 330 may
also be attenuated or suppressed. As a result, noise and vibration
generated in the lower scroll type compressor 10 may be
blocked.
[0078] In addition, the fixed scroll 320 is in face contact with
and supports the rotation shaft 230, so that durability of the
rotation shaft 230 may be reinforced even when the inflow force and
the gas force act on the rotation shaft 230.
[0079] In addition, a backpressure generated while the refrigerant
is discharged to outside is also partially absorbed or supported by
the rotation shaft 230, so that a force (normal force) in which the
orbiting scroll 330 and the fixed scroll 320 become excessively
close to each other in the axial direction may be reduced. As a
result, a friction force between the orbiting scroll 330 and the
fixed scroll 320 may be greatly reduced.
[0080] As a result, the compressor 10 attenuates the tilting in the
axial direction and the upsetting moment of the orbiting scroll 330
inside the compression assembly 300 and reduces the frictional
force of the orbiting scroll, thereby increasing an efficiency and
a reliability of the compression assembly 300.
[0081] In one example, the main frame 310 of the compression
assembly 300 may include a main end plate 311 provided at one side
of the driver 200 or at a lower portion of the driver 200, a main
side plate 312 extending in a direction farther away from the
driver 200 from an inner circumferential face of the main end plate
311 and seated on the fixed scroll 330, and a main shaft receiving
portion 318 extending from the main end plate 311 to rotatably
support the rotation shaft 230.
[0082] A main hole 317 for guiding the refrigerant discharged from
the fixed scroll 320 to the discharging portion 121 may be further
defined in the main end plate 311 or the main side plate 312.
[0083] The main end plate 311 may further include an oil pocket 314
that is engraved in an outer face of the main shaft receiving
portion 318. The oil pocket 314 may be defined in an annular shape,
and may be defined to be eccentric to the main shaft receiving
portion 318. When the oil stored in the sealing shell 130 is
transferred through the rotation shaft 230 or the like, the oil
pocket 314 may be defined such that the oil is supplied to a
portion where the fixed scroll 320 and the orbiting scroll 330 are
engaged with each other.
[0084] The fixed scroll 320 may include a fixed end plate 321
coupled to the receiving shell 110 in a direction away from the
driver 200 with respect to the main end plate 311 to form the other
face of the compression assembly 300, a fixed side plate 322
extending from the fixed end plate 321 to the discharging portion
121 to be in contact with the main side plate 312, and a fixed wrap
323 disposed on an inner circumferential face of the fixed side
plate 322 to define the compression chamber in which the
refrigerant is compressed.
[0085] In one example, the fixed scroll 320 may include a fixed
through-hole 328 defined to penetrate the rotation shaft 230, and a
fixed shaft receiving portion 3281 extending from the fixed
through-hole 328 such that the rotation shaft is rotatably
supported. The fixed shaft receiving portion 3331 may be disposed
at a center of the fixed end plate 321.
[0086] A thickness of the fixed end plate 321 may be equal to a
thickness of the fixed shaft receiving portion 3381. In this case,
the fixed shaft receiving portion 3281 may be inserted into the
fixed through-hole 328 instead of protruding from the fixed end
plate 321.
[0087] The fixed side plate 322 may include an inflow hole 325
defined therein for flowing the refrigerant into the fixed wrap
323, and the fixed end plate 321 may include discharge hole 326
defined therein through which the refrigerant is discharged. The
discharge hole 326 may be defined in a center direction of the
fixed wrap 323, or may be spaced apart from the fixed shaft
receiving portion 3281 to avoid interference with the fixed shaft
receiving portion 3281, or the discharge hole 326 may include a
plurality of discharge holes.
[0088] The orbiting scroll 330 may include an orbiting end plate
331 disposed between the main frame 310 and the fixed scroll 320,
and an orbiting wrap 333 disposed below the orbiting end plate to
define the compression chamber together with the fixed wrap 323 in
the orbiting end plate.
[0089] The orbiting scroll 330 may further include an orbiting
shaft receiving portion 338 defined through the orbiting end plate
331 to rotatably couple the rotation shaft 230.
[0090] The rotation shaft 230 may be disposed such that a portion
thereof coupled to the orbiting shaft receiving portion 338 is
eccentric. Thus, when the rotation shaft 230 is rotated, the
orbiting scroll 330 moves in a state of being engaged with the
fixed wrap 323 of the fixed scroll 320 to compress the
refrigerant.
[0091] Specifically, the rotation shaft 230 may include a main
shaft 231 coupled to the driver 200 and rotating, and a bearing
portion 232 connected to the main shaft 231 and rotatably coupled
to the compression assembly 300. The bearing portion 232 may be
included as a member separate from the main shaft 231, and may
accommodate the main shaft 231 therein, or may be integrated with
the main shaft 231.
[0092] The bearing portion 232 may include a main bearing portion
232c inserted into the main shaft receiving portion 318 of the main
frame 310 and rotatably supported, a fixed bearing portion 232a
inserted into the fixed shaft receiving portion 3281 of the fixed
scroll 320 and rotatably supported, and an eccentric shaft 232b
disposed between the main bearing portion 232c and the fixed
bearing portion 232a, and inserted into the orbiting shaft
receiving portion 338 of the orbiting scroll 330 and rotatably
supported.
[0093] In this connection, the main bearing portion 232c and the
fixed bearing portion 232a may be coaxial to have the same axis
center, and the eccentric shaft 232b may be formed such that a
center of gravity thereof is radially eccentric with respect to the
main bearing portion 232c or the fixed bearing portion 232a. In
addition, the eccentric shaft 232b may have an outer diameter
greater than an outer diameter of the main bearing portion 232c or
an outer diameter of the fixed bearing portion 232a. As such, the
eccentric shaft 232b may provide a force to compress the
refrigerant while orbiting the orbiting scroll 330 when the bearing
portion 232 rotates, and the orbiting scroll 330 may be disposed to
regularly orbit the fixed scroll 320 by the eccentric shaft
232b.
[0094] However, in order to prevent the orbiting scroll 320 from
rotating, the compressor 10 of the present disclosure may further
include an Oldham's ring 340 coupled to an upper portion of the
orbiting scroll 320. The Oldham's ring 340 may be disposed between
the orbiting scroll 330 and the main frame 310 to be in contact
with both the orbiting scroll 330 and the main frame 310. The
Oldham's ring 340 may be disposed to linearly move in four
directions of front, rear, left, and right directions to prevent
the rotation of the orbiting scroll 320.
[0095] In one example, the rotation shaft 230 may be disposed to
completely pass through the fixed scroll 320 to protrude out of the
compression assembly 300. As a result, the rotation shaft 230 may
be in direct contact with outside of the compression assembly 300
and the oil stored in the sealing shell 130. The rotation shaft 230
may supply the oil into the compression assembly 300 while
rotating.
[0096] The oil may be supplied to the compression assembly 300
through the rotation shaft 230. An oil supply channel 234 for
supplying the oil to an outer circumferential face of the main
bearing portion 232c, an outer circumferential face of the fixed
bearing portion 232a, and an outer circumferential face of the
eccentric shaft 232b may be formed at or inside the rotation shaft
230.
[0097] In addition, a plurality of oil supply holes 234a, 234b,
234c, and 234d may be defined in the oil supply channel 234.
Specifically, the oil supply hole may include a first oil supply
hole 234a, a second oil supply hole 234b, a third oil supply hole
234c, and a fourth oil supply hole 234d. First, the first oil
supply hole 234a may be defined to penetrate through the outer
circumferential face of the main bearing portion 232c.
[0098] The first oil supply hole 234a may be defined to penetrate
into the outer circumferential face of the main bearing portion
232c in the oil supply channel 234. In addition, the first oil
supply hole 234a may be defined to, for example, penetrate an upper
portion of the outer circumferential face of the main bearing
portion 232c, but is not limited thereto. That is, the first oil
supply hole 234a may be defined to penetrate a lower portion of the
outer circumferential face of the main bearing portion 232c. For
reference, unlike as shown in the drawing, the first oil supply
hole 234a may include a plurality of holes. In addition, when the
first oil supply hole 234a includes the plurality of holes, the
plurality of holes may be defined only in the upper portion or only
in the lower portion of the outer circumferential face of the main
bearing portion 232c, or may be defined in both the upper and lower
portions of the outer circumferential face of the main bearing
portion 232c.
[0099] In addition, the rotation shaft 230 may include an oil
feeder 233 disposed to pass through a muffler 500 to be described
later to be in contact with the stored oil of the casing 100. The
oil feeder 233 may include an extension shaft 233a passing through
the muffler 500 and in contact with the oil, and a spiral groove
233b spirally defined in an outer circumferential face of the
extension shaft 233a and in communication with the supply channel
234.
[0100] Thus, when the rotation shaft 230 is rotated, due to the
spiral groove 233b, a viscosity of the oil, and a pressure
difference between a high pressure region S1 and an intermediate
pressure region V1 inside the compression assembly 300, the oil
rises through the oil feeder 233 and the supply channel 234 and is
discharged into the plurality of oil supply holes. The oil
discharged through the plurality of oil supply holes 234a, 234b,
234c, and 234d not only maintains an airtight state by forming an
oil film between the fixed scroll 250 and the orbiting scroll 240,
but also absorbs frictional heat generated at friction portions
between the components of the compression assembly 300 and
discharge the heat.
[0101] The oil guided along the rotation shaft 230 and supplied
through the first oil supply hole 234a may lubricate the main frame
310 and the rotation shaft 230. In addition, the oil may be
discharged through the second oil supply hole 234b and supplied to
a top face of the orbiting scroll 240, and the oil supplied to the
top face of the orbiting scroll 240 may be guided to the
intermediate pressure region through the pocket groove 314. For
reference, the oil discharged not only through the second oil
supply hole 234b but also through the first oil supply hole 234a or
the third oil supply hole 234d may be supplied to the pocket groove
314.
[0102] In one example, the oil guided along the rotation shaft 230
may be supplied to the Oldham's ring 340 and the fixed side plate
322 of the fixed scroll 320 installed between the orbiting scroll
240 and the main frame 310. Thus, wear of the fixed side plate 322
of the fixed scroll 320 and the Oldham's ring 340 may be reduced.
In addition, the oil supplied to the third oil supply hole 234c is
supplied to the compression chamber to not only reduce wear due to
friction between the orbiting scroll 330 and the fixed scroll 320,
but also form the oil film and discharge the heat, thereby
improving a compression efficiency.
[0103] Although a centrifugal oil supply structure in which the
lower scroll type compressor 10 uses the rotation of the rotation
shaft 230 to supply the oil to the bearing has been described, the
centrifugal oil supply structure is merely an example. Further, a
differential pressure supply structure for supplying oil using a
pressure difference inside the compression assembly 300 and a
forced oil supply structure for supplying oil through a trochoid
pump, and the like may also be applied.
[0104] In one example, the compressed refrigerant is discharged to
the discharge hole 326 along a space defined by the fixed wrap 323
and the orbiting wrap 333. The discharge hole 326 may be more
advantageously disposed toward the discharging portion 121. This is
because the refrigerant discharged from the discharge hole 326 is
most advantageously delivered to the discharging portion 121
without a large change in a flow direction.
[0105] However, because of structural characteristics that the
compression assembly 300 is provided in a direction away from the
discharging portion 121 with respect to the driver 200, and that
the fixed scroll 320 should be disposed at an outermost portion of
the compression assembly 300, the discharge hole 326 is disposed to
spray the refrigerant in a direction opposite to the discharging
portion 121.
[0106] In other words, the discharge hole 326 is defined to spray
the refrigerant in a direction away from the discharging portion
121 with respect to the fixed end plate 321. Therefore, when the
refrigerant is sprayed into the discharge hole 326 as it is, the
refrigerant may not be smoothly discharged to the discharging
portion 121, and when the oil is stored in the sealing shell 130,
the refrigerant may collide with the oil and be cooled or
mixed.
[0107] In order to prevent this, the compressor 10 of the present
disclosure may further include the muffler 500 coupled to an
outermost portion of the fixed scroll 320 and providing a space for
guiding the refrigerant to the discharging portion 121.
[0108] The muffler 500 may be disposed to seal one face disposed in
a direction farther away from the discharging portion 121 of the
fixed scroll 320 to guide the refrigerant discharged from the fixed
scroll 320 to the discharging portion 121.
[0109] The muffler 500 may include a coupling body 520 coupled to
the fixed scroll 320 and a receiving body 510 extending from the
coupling body 520 to define sealed space therein. Thus, the
refrigerant sprayed from the discharge hole 326 may be discharged
to the discharging portion 121 by switching the flow direction
along the sealed space defined by the muffler 500.
[0110] Further, since the fixed scroll 320 is coupled to the
receiving shell 110, the refrigerant may be restricted from flowing
to the discharging portion 121 by being interrupted by the fixed
scroll 320. Therefore, the fixed scroll 320 may further include a
bypass hole 327 defined therein allowing the refrigerant penetrated
the fixed end plate 321 to pass through the fixed scroll 320. The
bypass hole 327 may be disposed to be in communication with the
main hole 317. Thus, the refrigerant may pass through the
compression assembly 300, pass the driver 200, and be discharged to
the discharging portion 121.
[0111] The more the refrigerant flows inward from an outer
circumferential face of the fixed wrap 323, the higher the pressure
compressing the refrigerant. Thus, an interior of the fixed wrap
323 and an interior of the orbiting wrap 333 maintain in a high
pressure state. Accordingly, a discharge pressure is exerted to a
rear face of the orbiting scroll as it is, and the backpressure is
exerted toward the fixed scroll in the orbiting scroll,
reactionally. The compressor 10 of the present disclosure may
further include a backpressure seal 350 that concentrates the
backpressure on a portion where the orbiting scroll 320 and the
rotation shaft 230 are coupled to each other, thereby preventing
leakage between the orbiting wrap 333 and the fixed wrap 323.
[0112] The backpressure seal 350 is disposed in a ring shape to
maintain an inner circumferential face thereof at a high pressure,
and separate an outer circumferential face thereof at an
intermediate pressure lower than the high pressure. Therefore, the
backpressure is concentrated on the inner circumferential face of
the backpressure seal 350, so that the orbiting scroll 330 is in
close contact with the fixed scroll 320.
[0113] In this connection, considering that the discharge hole 326
is defined to be spaced apart from the rotation shaft 230, the
backpressure seal 350 may also be disposed such that a center
thereof is biased toward the discharge hole 326.
[0114] In addition, due to the backpressure seal 350, the oil
supplied from the first oil supply groove 234a may be supplied to
the inner circumferential face of the backpressure seal 350.
Therefore, the oil may lubricate a contact face between the main
scroll and the orbiting scroll. Further, the oil supplied to the
inner circumferential face of the backpressure seal 350 may
generate a backpressure for pushing the orbiting scroll 330 to the
fixed scroll 320 together with a portion of the refrigerant.
[0115] As such, the compression space of the fixed wrap 323 and the
orbiting wrap 333 may be divided into the high pressure region S1
inside the backpressure seal 350 and the intermediate pressure
region V1 outside the backpressure seal 350 on the basis of the
backpressure seal 350. In one example, the high pressure region S1
and the intermediate pressure region V1 may be naturally divided
because the pressure is increased in a process in which the
refrigerant is inflowed and compressed. However, since the pressure
change may occur critically due to a presence of the backpressure
seal 350, the compression space may be divided by the backpressure
seal 350.
[0116] In one example, the oil supplied to the compression assembly
300, or the oil stored in the oil storage space P of the casing 100
may flow toward an upper portion of the casing 100 together with
the refrigerant as the refrigerant is discharged to the discharging
portion 121. In this connection, because the oil is denser than the
refrigerant, the oil may not be able to flow to the discharging
portion 121 by a centrifugal force generated by the rotor 220, and
may be attached to inner walls of the discharge shell 120 and the
receiving shell 110. The lower scroll type compressor 10 may
further include collection passages respectively on outer
circumferential faces of the driver 200 and the compression
assembly 300 to collect the oil attached to an inner wall of the
casing 100 to the oil storage space of the casing 100 or the
sealing shell 130.
[0117] The collection channel may include a driver collection
channel 201 defined in an outer circumferential face of the driver
200, a compression assembly collection channel 301 defined in an
outer circumferential face of the compression assembly 300, and a
muffler collection channel 501 defined in an outer circumferential
face of the muffler 500.
[0118] The driver collection channel 201 may be defined by
recessing a portion of an outer circumferential face of the stator
210 is recessed, and the compression assembly collection channel
301 may be defined by recessing a portion of an outer
circumferential face of the fixed scroll 320. In addition, the
muffler collection channel 501 may be defined by recessing a
portion of the outer circumferential face of the muffler. The
driver collection channel 201, the compression assembly collection
channel 301, and the muffler collection channel 501 may be defined
in communication with each other to allow the oil to pass
therethrough.
[0119] As described above, because the rotation shaft 230 has a
center of gravity biased to one side due to the eccentric shaft
232b, during the rotation, an unbalanced eccentric moment occurs,
causing an overall balance to be distorted. Accordingly, the lower
scroll type compressor 10 of the present disclosure may further
include a balancer 400 that may offset the eccentric moment that
may occur due to the eccentric shaft 232b.
[0120] Because the compression assembly 300 is fixed to the casing
100, the balancer 400 is preferably coupled to the rotation shaft
230 itself or the rotor 220 disposed to rotate. Therefore, the
balancer 400 may include a central balancer 410 disposed on a
bottom of the rotor 220 or on a face f acing the compression
assembly 300 to offset or reduce an eccentric load of the eccentric
shaft 232b, and an outer balancer 420 coupled to a top of the rotor
220 or the other face facing the discharging portion 121 to offset
an eccentric load or an eccentric moment of at least one of the
eccentric shaft 232b and the outer balancer 420.
[0121] Because the central balancer 410 is disposed relatively
close to the eccentric shaft 232b, the central balancer 410 may
directly offset the eccentric load of the eccentric shaft 232b.
Accordingly, the central balancer 410 is preferably disposed
eccentrically in a direction opposite to the direction in which the
eccentric shaft 232b is eccentric. As a result, even when the
rotation shaft 230 rotates at a low speed or a high speed, because
a distance away from the eccentric shaft 232b is close, the central
balancer 410 may effectively offset an eccentric force or the
eccentric load generated in the eccentric shaft 232b almost
uniformly.
[0122] The outer balancer 420 may be disposed eccentrically in a
direction opposite to the direction in which the eccentric shaft
232b is eccentric. However, the outer balancer 420 may be
eccentrically disposed in a direction corresponding to the
eccentric shaft 232b to partially offset the eccentric load
generated by the central balancer 410.
[0123] As a result, the central balancer 410 and the outer balancer
420 may offset the eccentric moment generated by the eccentric
shaft 232b to assist the rotation shaft 230 to rotate stably.
[0124] FIGS. 3A to 3C illustrate a process in which the compressor
of the present disclosure compresses the refrigerant.
[0125] FIG. 3A illustrates the orbiting scroll, FIG. 3B illustrates
the fixed scroll, and FIG. 3C illustrates a process in which the
orbiting scroll and the fixed scroll type compress the
refrigerant.
[0126] The orbiting scroll 330 may include the orbiting wrap 333 on
one face of the orbiting end plate 331, and the fixed scroll 320
may include the fixed wrap 323 on one face of the fixed end plate
321.
[0127] In addition, the orbiting scroll 330 is provided as a sealed
rigid body to prevent the refrigerant from being discharged to the
outside, but the fixed scroll 320 may include the inflow hole 325
in communication with a refrigerant supply pipe such that the
refrigerant in a liquid phase of a low temperature and a low
pressure may inflow, and the discharge hole 326 through which the
refrigerant of a high temperature and a high pressure is
discharged. Further, the bypass hole 327 through which the
refrigerant discharged from the discharge hole 326 is discharged
may be defined in an outer circumferential face of the fixed scroll
320.
[0128] In one example, the fixed wrap 323 and the orbiting wrap 333
may be formed in an involute shape and at least two contact points
between the fixed wrap 323 and the orbiting wrap 333 may be formed,
thereby defining the compression chamber.
[0129] The involute shape refers to a curve corresponding to a
trajectory of an end of a yarn when unwinding the yarn wound around
a base circle having an arbitrary radius as shown.
[0130] However, in the present disclosure, the fixed wrap 323 and
the orbiting wrap 333 are formed by combining 20 or more arcs, and
radii of curvature of the fixed wrap 323 and the orbiting wrap 333
may vary from part to part.
[0131] That is, the compressor of the present disclosure is
disposed such that the rotation shaft 230 penetrates the fixed
scroll 320 and the orbiting scroll 330, and thus the radii of
curvature of the fixed wrap 323 and the orbiting wrap 333 and the
compression space are reduced.
[0132] Thus, in order to compensate for this, in the compressor of
the present disclosure, radii of curvature of the fixed wrap 323
and the orbiting wrap 333 immediately before the discharge may be
smaller than that of the penetrated shaft receiving portion of the
rotation shaft such that the space to which the refrigerant is
discharged may be reduced and a compression ratio may be
improved.
[0133] That is, the fixed wrap 323 and the orbiting wrap 333 may be
more severely bent in the vicinity of the discharge hole 326, and
may be more bent toward the inflow hole 325, so that the radii of
curvature of the fixed wrap 323 and the orbiting wrap 333 may vary
point to point in correspondence with the bent portions.
[0134] Referring to FIG. 3C, refrigerant I is flowed into the
inflow hole 325 of the fixed scroll 320, and refrigerant II flowed
before the refrigerant I is located near the discharge hole 326 of
the fixed scroll 320.
[0135] In this case, the refrigerant I is present in a region at
outer circumferential faces of the fixed wrap 323 and the orbiting
wrap 333 where the fixed wrap 323 and the orbiting wrap 333 are
engaged with each other, and the refrigerant II is enclosed in
another region in which the two contact points between the fixed
wrap 323 and the orbiting wrap 333 exist.
[0136] Thereafter, when the orbiting scroll 330 starts to orbit, as
the region in which the two contact points between the fixed wrap
323 and the orbiting wrap 333 exist is moved based on a position
change of the orbiting wrap 333 along an extension direction of the
orbiting wrap 333, a volume of the region begins to be reduced, and
the refrigerant I starts to flow and be compressed. The refrigerant
II starts to be further reduced in volume, be compressed, and
guided to the discharge hole 326.
[0137] The refrigerant II is discharged from the discharge hole
326, and the refrigerant I flows as the region in which the two
contact points between the fixed wrap 323 and the orbiting wrap 333
exist moves in a clockwise direction, and the volume of the
refrigerant I decreases and starts to be compressed more.
[0138] As the region in which the two contact points between the
fixed wrap 323 and the orbiting wrap 333 exist moves again in the
clockwise direction to be closer to an interior of the fixed
scroll, the volume of the refrigerant I further decreases and the
refrigerant II is almost discharged.
[0139] As such, as the orbiting scroll 330 orbits, the refrigerant
may be compressed linearly or continuously while flowing into the
fixed scroll.
[0140] Although the drawing shows that the refrigerant flows into
the inflow hole 325 discontinuously, this is for illustrative
purposes only, and the refrigerant may be supplied continuously.
Further, the refrigerant may be accommodated and compressed in each
region where the two contact points between the fixed wrap 323 and
the orbiting wrap 333 exist.
[0141] FIG. 4 illustrates a structure of an Oldham's ring of a
compressor according to an embodiment of the present
disclosure.
[0142] Referring to FIG. 4, the Oldham's ring of the compressor
according to the present disclosure includes a ring body 710
provided between the orbiting scroll 330 and the main frame 310,
and a plurality of keys 720 protruding from the ring body and
coupled to the orbiting scroll and the main frame. The ring body
710 may be seated on the main side plate 312 of the main frame and
may be constructed in a circle or ellipse shape or a track shape to
accommodate the backpressure seal 350 therein.
[0143] The plurality of keys 720 may include a frame key 720a
protruding from one face of the ring body and coupled to the main
frame, and a scroll key 720b protruding from the other face of the
ring body and coupled to the orbiting scroll.
[0144] The plurality of keys 720 may be constructed to protrude
from positions of the ring body corresponding to a radial direction
of the ring body or the minor axis and major axis directions,
respectively. For example, the frame key 720a may be constructed to
protrude from a portion corresponding to the major axis of the ring
body 710 in the same direction as the major axis direction. The
scroll key 720b may be constructed to protrude from a position
corresponding to the minor axis of the ring body 710 in a direction
opposite to the direction in which the frame key 720a
protrudes.
[0145] An extension line of a line between the plurality of frame
keys 720a and an extension line of a line between the plurality of
scroll keys 720b may be perpendicular to each other. The plurality
of frame keys 720a may be arranged in a parallel line to a line
extending from the center of the main shaft receiving portion 318
to the center of the backpressure seal 350.
[0146] The backpressure seal 350 may be constructed to receive an
oil or refrigerant therein to generate a back pressure for pushing
the orbiting scroll 330 to the fixed scroll 320. In this
connection, the discharge hole 327 of the fixed scroll 320 may be
spaced apart from the rotation shaft 230 because the rotation shaft
230 passes through the fixed scroll 320. That is, the discharge
hole 327 is defined in the fixed main plate 311 and is spaced apart
from the fixed shaft receiving portion 318. Since the refrigerant
is discharged from the discharge hole 327, a strong reaction force
may be generated in a radial direction of the discharge hole 327.
Accordingly, a center of the backpressure seal 350 may be
positioned in the discharge hole 327 such that the backpressure
seal 350 may press the orbiting scroll 330 toward the discharge
hole 327 to prevent the orbiting scroll 330 from vibrating.
[0147] The Oldham's ring 700 according to the present disclosure
may be oriented such that the major axis of the ring body 710 lies
in a direction in which the backpressure seal 350 is eccentric.
Therefore, the Oldham's ring 700 may easily reciprocate inside the
main frame 310 while receiving the eccentric backpressure seal
350.
[0148] The main frame 310 may include a plurality of main key
grooves 315 defined in the main end plate, into which the frame key
720a is inserted, respectively. The main key grooves 315 may be
arranged in a radial direction of the main shaft receiving portion
318 or may be arranged in a parallel manner and around the main
shaft receiving portion 318. The main key groove 315 may have a
length such that the frame key 720 is inserted therein to
reciprocate in the radial direction of the main end plate 311.
[0149] The main end plate 311 may have a circular inner
circumferential face. However, in one side of the main end plate
311, a collision-prevention groove 312a may be defined to receive
one end of the main key groove 315 or to prevent collision thereof
with the scroll key 720. The collision-prevention groove 312a may
be recessed in the inner circumferential face of the main side
plate 312 outwardly.
[0150] In one example, the Oldham's ring 700 according to the
present disclosure may have an asymmetrical structure with respect
to the radial direction, the major axis direction, or the minor
axis direction. For example, the Oldham's ring 700 may have an
asymmetrical structure with respect to the minor axis direction.
The ring body 710 may have an asymmetrical structure with respect
to a line extending between the plurality of scroll keys 720b. A
shortest distance L1 of one of the plurality of frame keys 720a and
the line extending between the plurality of scroll keys 720b may be
not equal to a shortest distance L2 of another of the plurality of
frame keys 720a and the line extending between the plurality of
scroll keys 720b. The frame key 720a spaced apart from the line
extending between the plurality of scroll keys 720b at a larger
spacing among the plurality of frame key 720a may be closer to the
center of the backpressure seal 350.
[0151] Hereinafter, the center of the backpressure seal 350 may be
defined as a center of an outer circumferential face of a total
area in which the backpressure seal 350 moves with respect to the
main frame.
[0152] The Oldham's ring 700 may be asymmetrically constructed such
that the frame key 720a spaced apart from the line extending
between the plurality of scroll keys 720b at a larger spacing among
the plurality of frame key 720a may be closer to the discharge hole
327. That is, the ring body 710 may be asymmetrically constructed
such that only one frame key 720a of the plurality of frame key
720a may be closer to the discharge hole 327 than other frame keys
may be.
[0153] Thus, one frame key 720a of the plurality of frame keys 720a
may be spaced apart from the main side plate 311 at a larger
spacing. One of the main key grooves 315 may be defined in the main
side plate 311 and may be spaced, at a larger spacing, from the
main shaft receiving portion 318. The frame key 720a which is
spaced apart from the backpressure seal 350 at the larger spacing
may be prevented from collision with the main side plate 311. As a
result, the main frame 310 may be free of the collision-prevention
groove 312a and thus maintain the inner circumferential surface of
the main side plate 312 to be continuously circular. Therefore, the
pressure is prevented from being generated non-uniformly in the
main frame 310 to increase the efficiency of the compressor and to
reduce vibration and noise.
[0154] Further, since the collision-prevention groove 312a is
removed, an area of the main collection channel 301a defined as a
D-CUT in the outer circumferential face of the main side plate 312
may be extended by an area A. Thus, a total cross-sectional area of
the oil collection channel of the compressor may be increased,
thereby to increase the oil collection ability. The area A may
correspond to an area required to space the collection channel 301a
from the groove 312a when the groove 312a is installed in the main
frame 310.
[0155] Therefore, the collection channel 301a may be disposed to
overlap at least one of the plurality of main key grooves 315 in
the radial direction of the rotation shaft. In other words, at
least one of the plurality of main key grooves 315 may overlap the
collection channel 301a in the radial direction.
[0156] In the compressor 10 according to the present disclosure,
the ring body 710 is asymmetrically constructed, and the frame keys
720a are arranged asymmetrically. Thus, the main key grooves 315
may be arranged in an asymmetrical manner with respect to the main
shaft receiving portion 318. The plurality of main key grooves 315
may be arranged asymmetrically around the rotation shaft 230.
[0157] Although not shown, the orbiting scroll 330 may include a
plurality of orbiting key grooves 335 defined in the orbiting end
plate 331, into which the scroll keys 720b are inserted,
respectively.
[0158] FIGS. 5A and 5B illustrate an Oldham's ring of a compressor
according to one embodiment of the present disclosure.
[0159] Referring to FIG. 5A, the Oldham's ring 700 may be
constructed to be shortened so that one end spaced farthest from
the backpressure seal 350 is closer towards the eccentric
backpressure seal.
[0160] The ring body 710 may be constructed to be shortened such
that one of the plurality of frame keys 720a is closer to another
frame key toward the eccentric backpressure seal 350. The ring body
710 may be constructed to be shortened such that one of the
plurality of frame key 720a spaced from the center of the
backpressure at a larger spacing is further closer to the frame key
720a spaced from the center of the backpressure seal at a smaller
spacing.
[0161] The ring body 710 may be constructed to be shortened such
that one of the plurality of frame key 720a spaced from the center
of the backpressure at a larger spacing is further closer, by a
distance L3 between the center of the backpressure seal and the
center of the rotation shaft, to the frame key 720a spaced from the
center of the backpressure seal at a smaller spacing.
[0162] In other words, the ring body 710 is constructed to be
shortened compared to a construction in which the ring body 710 is
symmetrically constructed about the minor axis. In this connection,
a maximum length by which one end of the ring body 710 to be
reduced or the frame key 720a may be reduced may be the distance L3
between the center of the backpressure seal and the center of the
rotation shaft. That is, the ring body 710 may be constructed to be
shortened such that one end of the major axis thereof is reduced
toward the eccentric backpressure seal 350. One end of the major
axis thereof may be constructed to be shortened by the distance L3
between the center of the backpressure seal and the center of the
rotation shaft.
[0163] An area occupied by the ring body 710 when the ring body 710
is constructed asymmetrically may be reduced compared to the area
thereof when the ring body 710 is constructed symmetrically. As a
result, the weight of the ring body 710 may be reduced. Since the
ring body 710 is mounted on the orbiting scroll 330 and acts as a
load on the driver 200, the efficiency of the compressor may be
further increased due to the weight reduction of the ring body 710.
When the ring body 710 has one end shortened by the length of L3
while the other end thereof is not shortened, the weight of the
ring body 710 may be greatly reduced.
[0164] In one example, the ring body is constructed such that the
minor axis thereof is orthogonal to the major axis thereof. Both
ends of the minor axis are constructed to be shortened to a
diameter of the backpressure seal or to the outer circumferential
face of a total area in which the backpressure seal 350 moves. That
is, a distance between a plurality of the scroll keys 720a may be
defined in a corresponding manner to an area within which the
backpressure seal 350 may move. As a result, the length of the
minor axis of the ring body 710 may be minimized, thereby reducing
the area occupied by the Oldham's ring and the weight thereof to
the maximum degree.
[0165] In other words, the Oldham's ring 700 may be constructed
such that one end thereof spaced farthest from the backpressure
seal 350 is closer toward the minor axis than the other end is. The
Oldham's ring 700 includes the ring body 710 having, as the major
axis thereof, an extension line of a line between the center of the
backpressure seal 350 and the center of the rotation shaft 230
between the orbiting scroll and the main frame. The ring body 710
may be constructed such that one end of the major axis thereof
spaced furthest from the eccentric backpressure seal 350 is closer
to the minor axis and toward the eccentric backpressure seal than
the other end is. One end of the major axis thereof may be closer
to the minor axis than the other end is by the distance L3 between
the center of the rotation shaft and the center of the backpressure
seal.
[0166] One of the plurality of frame key 720a may be constructed to
be closer to the backpressure seal than another frame key is. In
other words, the frame key constructed to be spaced from the center
350a of the backpressure seal at a larger spacing among the
plurality of frame keys 720a may be constructed to be closer to the
minor axis such that the frame key is further closer to a frame key
constructed to be spaced from the center 350a of the backpressure
seal at a smaller spacing. A distance by which one of the plurality
of frame keys 720a is further closer to the minor axis may
correspond to the distance L3 between the center 350a of the
backpressure seal and the center 230a of the rotation shaft.
[0167] A distance between both ends of the minor axis of the ring
body 710 may correspond to a diameter of an outer circumferential
face of a space in which the backpressure seal 350 moves.
[0168] Referring to FIG. 5B, the ring body 710 may move inside the
main frame 310 based on a direction of the main key groove 315
according to the movement of the orbiting scroll 330. In this
connection, the key groove 315a corresponding to the frame key 720a
disposed on the shortened portion of the ring body 710 among the
main key grooves may be further spaced apart from the main side
plate 312.
[0169] The key groove 315a may be constructed such that one end
thereof contacts an outer circumferential face of an area in which
the backpressure seal 350 moves. Accordingly, even when the
collision-prevention groove 312a is omitted from the main frame
310, collision between the frame key 720a and the main side plate
312 may be prevented. Further, the area of the main channel 301a
may be increased as much as possible.
[0170] Hereinafter, another embodiment of a compressor according to
the present disclosure will be described with reference to FIG.
6.
[0171] FIG. 6 illustrates an orbiting scroll of a compressor
according to the present disclosure.
[0172] The orbiting scroll 330 according to the present disclosure
may include an orbiting shaft receiving portion 338 through which
the rotation shaft 230 passes and a sealing groove 336 on which the
back pressure seal 350 is seated.
[0173] In the compressor according to one embodiment of the present
disclosure as shown in FIGS. 5A and 5B, the main key grooves 315
are arranged on an extension line D between a center 336a of the
sealing groove 336 and a center 338a of the orbiting shaft
receiving portion 338. Orbiting key grooves 335 in which the scroll
key 720b is inserted may be arranged in a line perpendicular to the
line D.
[0174] However, the compressor according to another embodiment of
the present disclosure shown in FIG. 6, the extension line D1
between the plurality of main key grooves 315a may be spaced, by an
angular spacing "a", the extension line D between the center 336a
of the sealing groove 336 and the center 338a of the orbiting shaft
receiving portion 338 on which the main key grooves 315 are
arranged.
[0175] The ring body 710 may be constructed such that the major
axis line D1 thereof is spaced, by an angular spacing "a", from the
extension line D between the center 336a of the sealing groove 336
and the center 338a of the orbiting shaft receiving portion 338.
Thus, a plurality of frame key 720a may be arranged in a line
misaligned with the eccentric portion of the backpressure seal 350.
In other words, the plurality of frame key 720a may be arranged in
a line spaced by a certain angular spacing from the extension line
D between the center of the backpressure seal and the center of the
main shaft receiving portion 318.
[0176] Thus, the orbiting scroll 330 may be constructed to
reciprocate in the main frame 310 in a direction different from the
direction D in which the backpressure seal 350 is eccentric.
Further, the major axis and the minor axis of the ring body 710 may
not correspond to the direction D in the main frame 310 in which
the backpressure seal 350 is eccentric.
[0177] FIG. 7 illustrates a main frame to which the Oldham's ring
structure of FIG. 6 is applied.
[0178] Referring to FIG. 7, the Oldham's ring 700 may be disposed
in the main frame 310 and may have an asymmetrical structure with
respect to an extension line D between the center of the
backpressure seal 350 and the center of the main shaft receiving
portion 318. In other words, the major axis D1 of the ring body 710
may be spaced by a certain angular spacing, from the extension line
D.
[0179] The backpressure seal 350 is eccentrical around the main
shaft receiving portion 318 and is biased toward the main side
plate 312. Thus, the shortest distance H1 between the main side
plate 312 and the outer circumferential face defined by the area in
which the backpressure seal 350 moves in the main end plate 311 may
be smaller than another distance between the main side plate 312
and the outer circumferential face defined by the area in which the
backpressure seal 350 moves. Further, the shortest distance H1 may
be smaller than a length H2 of the main key groove 315. Therefore,
when the main key groove 315 is installed at a portion of the main
frame corresponding to the shortest distance H1, the
collision-prevention groove 312a should be defined in the main
frame.
[0180] However, in the compressor according to the present
disclosure, the Oldham's ring 700 may be constructed such that the
major axis D1 of the ring body 710 may be inclined with respect to
the extension line D. In this connection, the major axis D1 of the
ring body 710 is positioned at a position such that a distance
between the outer circumferential face defined by the area in which
the backpressure seal 350 moves and the main side plate 312 is
greater than or equal to the length H2 of the main key groove 315.
A position defined such that the distance between the outer
circumferential face defined by the area in which the backpressure
seal 350 moves and the main side plate 312 is equal to the length
H2 of the main key groove 315 is spaced, by an angular spacing "a"
angle, from the extension line D around the rotation shaft 230.
Accordingly, the major axis D1 of the ring body 710 may be spaced,
by an angular spacing greater than or equal to the angle "a" from
the extension line D.
[0181] Thus, the main key groove 315 may not be installed at a
portion corresponding to the shortest distance H1. In the
compressor according to the present disclosure, a new main key
groove 315b may be defined at a point where a length of the inner
circumferential face of the main side plate 312 and a length of the
outer circumferential face defined by the area in which the
backpressure seal 350 moves is equal to or greater than H2. The
other main key grooves 315b may be arranged in a parallel line to
the longitudinal direction of the main key groove 315b.
[0182] In other words, in the main frame 310 of the compressor
according to the present disclosure, an installation position of
the main key groove 315b may be changed such that an extension line
of a line between the main key grooves 315b may be spaced, by an
angular spacing greater than or equal to the angle "a" from the
extension line of a line between the center of the backpressure
seal 350 and the center of the main shaft receiving portion
318.
[0183] As such, the Oldham's ring 700 according to the present
disclosure may be constructed such that the plurality of frame keys
720 are arranged in a line inclined relative to the extension line
D between the center of the backpressure seal 350 and the center of
the rotation shaft 230. As a result, the main key groove 315b may
be installed in the main end plate 311 without being affected by
the backpressure seal 350, and thus the entire inner
circumferential surface of the main side plate 312 may define a
continuous surface. That is, the entire inner circumferential
surface of the main side plate 312 may be constructed to form a
complete continuous circle. As a result, the collision-prevention
groove 312a may not be defined in the inner circumferential surface
of the main side plate 312. Therefore, a symmetrical pressure
gradient is created in the main frame 310 and around the main shaft
receiving portion 318 to improve compression efficiency and reduce
vibration and noise.
[0184] Effects as not described herein may be derived from the
above configurations. The relationship between the above-described
components may allow a new effect not seen in the conventional
approach to be derived.
[0185] In addition, embodiments shown in the drawings may be
modified and implemented in other forms. The modifications should
be regarded as falling within a scope of the present disclosure
when the modifications is carried out so as to include a component
claimed in the claims or within a scope of an equivalent
thereto.
* * * * *